Drive rod support assembly with torque support and industrial gear equipped therewith, and method for adjusting a drive rod support assembly and use

Abstract

The invention relates to a drive train mounting assembly for industrial transmissions, in particular for a double-mounted or torque-mounted rotor of a wind turbine, comprising a mounting, which is supported / can be supported in a first housing, for a shaft of the drive train, and a transmission component which is surrounded by a second housing and is coupled to the shaft, and a torque support which counteracts at least one gravity-induced torque acting on the shaft by means of the transmission component; wherein the torque support is supported on or fastened to the (first) housing of the mounting of the shaft. The invention further relates to corresponding methods or mounting types and uses.

Description

TECHNICAL AREA

[0001] The invention relates to a wind turbine with an industrial gearbox comprising a bearing supported in a first housing for a shaft of the drive train and a gearbox component surrounded by a second housing and coupled to the shaft, and a torque support, wherein the torque support counteracts at least one moment acting on the shaft and caused by gravity on the part of the gearbox component; the invention further relates to a drive train and an industrial gearbox with such a bearing. BACKGROUND OF THE INVENTION

[0002] In drive trains where comparatively massive and large components are interconnected, high forces act solely due to gravity, which can also have a very dynamic impact on the drive train and the corresponding bearing components. Depending on the dynamics and load range, it may be necessary to brace individual components against gravity and / or secure them against excessive dynamic load peaks. For example, in wind turbines, the dynamic forces and moments are particularly relevant due to the unpredictable operating and weather conditions, placing considerable stress on the components, especially in offshore installations, which are designed for a long service life. Therefore, improving the existing conditions and options for minimizing structurally stressful forces and moments is desirable.

[0003] For some applications, particular attention must also be paid to so-called cyclic bending moments: If the drivetrain is subjected to a static load on one side by large masses with high leverage (for example, in addition to dynamic wind events), this leads to a dynamic load or cyclic stress on the rotating components, such as the rotor shaft, a planet carrier, especially of a first gear stage, and / or rotating connecting elements, e.g., in flange design, due to a very large diameter rotor of a wind turbine, which may also be rotating at a rather unfavorable frequency / rotation rate. This can lead to very severe impacts on the structure, the machine frame, and the entire assembly, including bearings and any couplings. Therefore, there is great interest in minimizing such cyclic bending moments, especially in connection with increasing system power and component weights.

[0004] Previously, the primary approach was to over-dimension the affected components, resulting in significant cost and material expenditure, particularly based on comparatively large safety factors. Previously, especially heavy or bulky components, or particularly protruding drivetrain components, were typically supported in the direction of the machine carrier (base), especially in the area of ​​a generator located further away from the rotor behind a transmission component (torque support unit or weight force support with coupling to the base).

[0005] Publication US 2016 / 061191 A1 describes a claw-type coupling for wind turbine drive trains at the interface between a planetary ring gear face and a shaft flange supported against a base, with vibration dampers provided on the claw flanks. EP 2 630 372 A1 shows an arrangement with a rotor bearing and a gearbox housing rigidly coupled to it. The rotating parts, namely the rotor shaft and the gearbox input shaft, are connected to each other via a flexible coupling.

[0006] Based on this, there is a need for optimized measures for torque or weight force support of drivetrain components, e.g. gearbox stage and / or generator, especially also in drivetrains for wind turbines. SUMMARY OF THE INVENTION

[0007] The object of the present invention is to demonstrate measures that enable improved torque or weight force support of comparatively massive, heavy drivetrain components, in particular of gearbox stages and / or generators, especially also in drivetrains for wind turbines.

[0008] The problem is solved by a wind turbine with an industrial gearbox having the features of claim 1, and by a method according to the features of the dependent method claim.

[0009] Preferred embodiments are specified in the dependent claims and in the following description, each of which, individually or in combination, can represent an aspect of the invention. When a feature is presented in combination with another feature, this serves only to simplify the presentation of the invention and is in no way intended to imply that this feature cannot also be a further development of the invention without the other feature.

[0010] One aspect of the invention relates to a drivetrain bearing arrangement in connection with drivetrains subjected to a dynamic and comparatively large moment, in particular a tilting moment. A drivetrain bearing arrangement for industrial gearboxes, in particular for a double-bearing or moment-bearing rotor of a wind turbine, is provided, comprising: a bearing supported / supportable in a first housing (in particular with two axially offset bearing points) for a shaft of the drivetrain, and a gearbox component with a planetary gear stage, surrounded by a second housing and coupled / connected to the shaft.

[0011] According to the invention, a moment support is proposed to counteract a gravity-induced (tilting) moment acting on the shaft from the gearbox component (in particular, a moment or rotational bending resulting from a gearbox-generator combination); wherein the moment support is attached to the (first) housing of the shaft bearing. This enables a considerable reduction in the static and dynamic loads exerted on the drivetrain or on the components rigidly connected to one another (shaft, gearbox, any couplings). For example, in a wind turbine with a double-bearing rotor shaft or so-called moment bearing and a gearbox and generator connected to it, the rotational bending resulting from the weight of the gearbox-generator combination can be noticeably reduced.There are also advantages in terms of design, especially regarding the stiffness and size requirements of a machine carrier.

[0012] The weight of the gearbox and any generator optionally flanged to the gearbox housing typically stresses the rotor shaft, rotor bearings, gearbox components (especially a planet carrier of a first gearbox stage and its planet carrier bearings), and any flange connections between the gearbox and generator. This results in so-called rotating bending stress in the rotating elements, which must be taken into account in the dimensioning and design of the overall structure. Against this background, the present invention makes it possible to significantly reduce the rotating bending stress and simultaneously also reduce tilting in the gearbox, particularly in a / the first planetary stage. This also leads to improved load-bearing capacity of the gearbox gears. The reduction in structural stresses achievable according to the invention can therefore also be accompanied by reduced wear.

[0013] The present invention also enables optimized force return with comparatively low negative effects from various deformations in / on the machine support and in / on the gearbox, in particular thanks to the support of both the gearbox torque and weight leverage forces by means of torque support via the rotor bearing housing. For example, in wind turbines, the pitching moments acting on the rotor and the rotor shaft due to wind loads can be absorbed in an optimized manner even if the orientation of the shaft and any other components of the drive train is at least slightly altered by, for example, a slightly tilting rotor; in particular, these pitching moments no longer need to be transferred via the machine support as before, so that no additional loads need to be absorbed in the supporting structure.Rather, the present invention also allows for at least a small tolerance of movement, depending on the type of support on the first housing. The present invention can be advantageously implemented in various types of drive trains, particularly in cases of comparatively large pitching moments. By way of example, a drive train with planetary gearheads, especially in roller presses, can be mentioned as a further possible application.

[0014] In previous gearboxes, support was typically provided downwards towards the base / machine frame. Up to now, the resulting rotating bending moments and pitching moments were often absorbed by oversizing the affected machine elements (especially the rotor shaft, rotor bearings, gearbox stage including, for example, the planet carrier, planet carrier bearings, and gearbox and generator housing flanges). However, this approach results in a considerable cost and weight disadvantage, and in wind turbines, for example, the weight disadvantage can also have a very detrimental effect on other system components, such as the wind turbine tower, which then needs to be designed with correspondingly higher load-bearing capacity. To better meet these requirements, a weight-force support between the generator and the machine frame has also been used previously.However, one disadvantage is that the supporting structure below the generator is usually not designed for this purpose, and additional load increases can occur during a rapid pitching movement of the drive train; this also puts additional strain on the flange connections between the gearbox and generator.

[0015] In contrast, according to the invention, the knowledge is used that the power flow can also be captured and diverted via the rotor bearing housing; the gear stage with generator can optionally also be arranged "floating" (in particular, suspended freely on one side in space), in the manner of a free end of the drive train, which experiences a certain movement tolerance, i.e., for example, a predefined maximum amount of a pitching movement, even together with the rotor.the shaft can / could be designed to achieve a considerable degree of freedom of movement in several spatial directions, depending on the application and the desired or required stiffness of the drive train. Depending on the desired stiffness, the support on the rotor bearing housing can be individually designed with respect to specific directions of movement, for example, regarding the magnitude of the movement tolerance, preload, damping (especially by means of elastomer bearings), or the like. Vibration decoupling can also be achieved, particularly at the interface between the first and second housings. This is also relevant in connection with, for example,In wind turbines, where very dynamic external influences (wind / weather, rotor blade adjustment or similar changes to the system / operating state) occur, the invention also enables a very sustainable and material-efficient method of bearing, which is also suitable for a slim, weight-optimized design.

[0016] The moment support can be distributed around the circumference of the rotor bearing housing and may, for example, have one or more supports, particularly on individual circumferential sections. The person skilled in the art can select the most advantageous support method in each individual case, depending on the other components of the respective drive train, and especially based on the present disclosure.

[0017] In the following, "axial" refers in particular to an alignment along the length of the shaft or another component of the drivetrain coupled axially to it. Depending on the inclination of the drivetrain, an "axial" alignment can also be at least approximately horizontal, especially along the length between the rotor or hub on the one hand and the gearbox component or generator on the other. According to one embodiment, the drivetrain described here is bounded on one side by the rotor and on the other side by the gearbox component or a generator (optionally coupled directly to the gearbox).

[0018] When the term "rotor bearing" is used, it can also refer to other shaft bearings; the term "rotor bearing" is chosen here to illustrate that the bearing is located in the section of the shaft where the forces and moments exerted on the shaft by a rotor are supported. The rotor bearing in wind turbines, for example, is comparatively robust, strong, and voluminous, especially since the rotor can have a diameter of many meters (even over 100m or 200m) and can therefore be the cause of very high stresses and moments.

[0019] Personalized terms, unless explicitly formulated in the neuter gender, may refer to all genders within the context of this disclosure. Any English terms or abbreviations used herein are standard industry terms and are familiar to those skilled in the art. Any synonymous German terms may be indicated here in parentheses for the sake of completeness, or vice versa.

[0020] If, according to the present disclosure, reference is made to a vertical direction or a direction of gravity, this is aligned at an angle of (depending on the inclination of the shaft or of one / the rotor) at least approximately 90° to the axial direction of the drive train or to its intended installation position (center lines or the axis of rotation of the respective transmission component or the power shaft in a horizontal direction or slightly inclined thereto).

[0021] Where the present disclosure refers to a planetary gear system, it may refer to planetary gear stages in general as well as to planetary spur gear systems.

[0022] According to the present disclosure, the tilting moment is to be understood as a moment which results from the weight of the gearbox and, if applicable, additionally from the weight of the generator, multiplied by the lever arm to the support / pivot point on the planet carrier bearing or at an interface between the gearbox and the rotor shaft (as well as any additional dynamic loads occurring during operation).

[0023] It has been shown that the present invention is particularly advantageous in connection with integrated planetary gearboxes or planetary gearbox stages, especially when a generator is also mounted uniaxially or in alignment with the gearbox. Nevertheless, the advantages described here can also be realized for drive trains with other or additional gearbox types / stages.

[0024] According to one embodiment, the at least one adjustable unit generates a first substantially axially oriented force couple F1 around the axial center of the drive train at at least one circumferential position pair, in particular at 06 and 12 o'clock and / or at 03 and 09 o'clock, in particular a force couple F1 directed against tilting and / or yaw moments.

[0025] According to one embodiment, the at least one adjustable unit generates a second, essentially radially / tangentially oriented torque-generating force couple F2 at at least one pair of circumferential positions, in particular at 3 and 9 o'clock and / or at 6 and 12 o'clock, acting orthogonally to the axial center of the drive train, in particular a force couple F2 directed against torques around the shaft. In other words: The at least one adjustable unit is arranged at at least one pair of circumferential positions to generate a counter-torque about the corresponding spatial axis.

[0026] According to one embodiment, the at least one adjustable unit ensures vibration damping or vibration decoupling at at least two opposing circumferential positions in at least one coupling section between interacting coupling parts, in particular by means of at least one preload unit per circumferential position.

[0027] According to one embodiment, the at least one adjustable unit is installed at at least two opposing predefined circumferential positions, in particular at least at the circumferential positions 6 and 12 o'clock and / or 3 and 9 o'clock, acting in a spring-like and / or damping manner between tie rods or tension / compression anchors of the gearbox housing and the rotor bearing housing, respectively. The respective opposing circumferential positions can also be selected depending on the prevailing load conditions and, for example, scaled in number and size.

[0028] According to one embodiment, the drivetrain mounting arrangement comprises a plurality of adjustable units by means of which reaction force pairs are provided around all three moment axes or acting three-dimensionally around all three spatial directions and can optionally be actively adjusted. This also provides particularly effective damping.

[0029] According to one embodiment, the torque support is supported exclusively on the first housing or on the housing of the shaft bearing, independent of any connection to a machine support or similar base located below the drivetrain or below the drivetrain bearing assembly. This also allows for a degree of movement tolerance without requiring the machine support to have a comparatively large axial length and / or a comparatively robust design.

[0030] According to one embodiment, the moment support is provided at support points / areas arranged along an outer connection diameter between the first and second housings on the (first) housing of the shaft bearing, in particular in at least four circumferential sections or completely on the first housing, especially with a rotationally symmetrical distribution of the support points / areas over the entire circumference. This also enables, among other things, an optimization of the transmission of forces and moments largely independent of their direction of action.

[0031] According to one embodiment, the first and / or the second housing at least partially provides at least one coupling partner (claw, cam, pin, web, or similar projection, particularly also in the radial and / or tangential direction or circumferential direction) for mutual support of the housings, especially in a one-piece integral design on an outer surface of the respective housing. This also provides good robustness. With an even distribution of the coupling partners (elements) in the circumferential direction, support can also be ensured largely independently of the instantaneous direction of force / torque.

[0032] The moment support has at least one adjustable unit, in particular a unit adjustable with respect to force (magnitude) and / or direction of action and / or point / area of ​​force application. This also facilitates the individualization of the support method, for example, with regard to operating-condition-dependent control.

[0033] The adjustable unit can be adjustable, for example, with respect to a preload force (in particular spring force or hydraulic force) and / or with respect to an active control force (counterforce) in response to sensor-detected instantaneous forces and torques. Corresponding sensors are provided, for example, in the area of ​​the respective interface on end-face and / or radial contact surfaces. In this respect, the present invention also provides a concept for the active application of force, particularly in response to forces / torques currently acting on the drive train, e.g., depending on prevailing wind / weather conditions in offshore wind turbines.

[0034] According to one embodiment, the moment support, in particular at least one adjustable unit of the moment support, is provided in an upper and / or lower region of an interface between the housings. Such an arrangement also offers the advantage that a righting and / or supporting force can be applied selectively to specific circumferential sections. With regard to the righting force described here, due to the associated advantageous lever arm, a point of force application is provided at the bottom and top of the corresponding connection diameter on the housing, or even further radially outward at specially provided tabs, pins, or similar lever elements.

[0035] For example, the force transmission with respect to the desired erection force (essentially horizontal) occurs over a circumferential angle range of at least twice 30° and / or in combination with a possibly desired or possibly only very locally intended support force (essentially vertical) over a circumferential angle range of at least four times 20°. Depending on the number and design of the force-transmitting sections, however, a shorter or narrower element may also suffice, e.g., in a circumferential segment over an angle of only 10°.

[0036] According to one embodiment, the moment support, in particular the at least one adjustable unit, is diagonally configured, especially such that hydraulic or mechanical compensation is relatively soft in the axial direction and relatively stiff in the tilting direction. This also promotes a good compromise between effective support and potentially desired positional tolerance compensation, particularly in connection with manufacturing tolerances, rotor bearing clearance, or rotor bearing compliance in the axial direction.

[0037] The at least one adjustable unit, or at least one adjustable element thereof, can be diagonally connected in such a way that a hydraulic or mechanical compensation is relatively soft in the axial direction of the axis of rotation and relatively stiff in the tilting direction, in particular such that in the tilting direction a hydraulic or mechanical compensation is designed to be softer or stiffer, or with higher or lower vibration damping, depending on the direction. This also results in advantageous operating characteristics.

[0038] The moment support can be hydraulically and / or mechanically supported, particularly in a circumferential angle range of at least twice 30° and / or in a circumferential angle range of at least four times 20°, such that a hydraulic or mechanical compensation in the axial direction of the axis of rotation is relatively soft and in the circumferential direction relatively stiff, in particular such that in the circumferential direction a hydraulic or mechanical compensation is designed to be directionally softer or stiffer or with higher or lower vibration damping.

[0039] The present invention enables several combinable measures not only relating to tilting moment support but also to torque support. The latter acts circumferentially and can be required or adjusted / controlled depending on the power output. The tilting moment support counteracts the force of gravity in the tilting direction and can therefore also be described as a counterforce or restoring force with a vertical force component.

[0040] According to one embodiment, a radially projecting flange or similar force application ring or segment is provided on the (second) housing of the transmission component, which is bounded or encompassed by the moment support, in particular by the at least one adjustable unit, at at least one axial position (in particular, axially opposite on both sides), for example, in a ring-like manner in the form of a C-shaped ring shell or several (half-)shell elements. This also allows for the advantageous provision of a very robust arrangement with a certain angular tolerance and, for example, an integrated damping function.

[0041] The respective point / area of ​​force application can, for example, be integrally integrated into the respective housing component, such as cast into the housing in the case of cast housings, and thus already considered during the design and dimensioning phases. Alternatively (e.g., if a cast housing is not used) or additionally, a reversible form-fit / force-fit connection type can be provided, such as a screw connection. This is useful, for example, in connection with a retrofit or upgrade option in existing gearboxes or on already installed drive trains, where a material-fit fastening is also possible.

[0042] According to one embodiment, the moment support is arranged such that a righting force acting essentially axially and against the tilting moment is provided on the second housing, particularly in a force application area located as far out radially as possible on the housing of the transmission component. The righting force is provided, for example, by a force couple at opposing force application areas located as far out radially as possible, so that even small movement tolerances can be compensated for as precisely as possible, with a good lever arm, and optionally with damping. Here, "axial" is also to be understood in the sense of the axial extent of the drive train.

[0043] According to one embodiment, the torque support comprises a (further) support unit acting on the (first) housing of the shaft bearing, which is arranged such that a force acting essentially vertically (radially / tangentially) or circumferentially is provided / is provided to act on the second housing. This also enables further functional integration into the torque support, particularly with regard to torques acting around the shaft or the drive train and with regard to any positional tolerance or damping that may be desired in this respect.

[0044] In this respect, the present invention also provides moment support in a radial plane in the tangential direction or in the circumferential direction (torque support in the manner of an inner support) and tilt support out of the radial plane (in the manner of an outer support), in each case by support on the solid rotor bearing housing, whereby the underlying machine support can be designed to be less massive or more slender. The force compensation can be achieved, for example, hydraulically.

[0045] According to one embodiment, the second housing is arranged separately and axially spaced from the first housing. The housings are directly connected to each other, for example exclusively by means of the moment support described here, and only indirectly via the respective bearings and shafts provided in each housing.

[0046] According to one embodiment, the transmission component is arranged between the shaft and a generator, which acts on the second housing or on the transmission component (or its weight force). This type of series connection in the drivetrain has proven advantageous for various applications, and according to the invention, the support can also be advantageously implemented with an additionally flanged generator, in particular solely by support on the first housing, i.e., without further supports towards the machine carrier. This also allows for a comparatively short / slender machine carrier, even with a generator arranged in series, and thus also an advantageous force distribution / concentration on the interface to the bearing housing.

[0047] One aspect of the invention further relates to an industrial gearbox with such a drive train bearing arrangement, in particular in an arrangement in a wind turbine.

[0048] The aforementioned problem is also solved by an industrial gearbox, particularly one with a planetary gear stage, featuring a drivetrain bearing arrangement described above. Similarly, the aforementioned problem is also solved by a wind turbine equipped with such an industrial gearbox or drivetrain bearing arrangement. This results in the aforementioned advantages, particularly regarding the gearbox's operation under significantly reduced external loads and with significantly reduced wear.

[0049] A further aspect of the invention relates to a method for adjusting or adapting the bearing of such a drivetrain bearing arrangement. The aforementioned problem is also solved by a method according to the corresponding dependent claim, namely by a method for adjusting the bearing of a drivetrain bearing arrangement of an industrial gearbox, in particular in a drivetrain with a double-bearing or torque-bearing rotor of a wind turbine, wherein a bearing of a shaft of the drivetrain supported in a first housing and a gearbox component (in particular a planetary gear stage) surrounded by a second housing and coupled to the shaft are / are supported relative to each other, wherein a torque support, which counteracts a gravity-induced torque acting on the shaft from the gearbox component,The second housing, and thus the gearbox component, is supported by the first housing, i.e., the housing of the shaft bearing. This is particularly relevant in a drivetrain with a generator supported by the second housing and therefore also by the first housing, especially in a drivetrain bearing arrangement described above, or in an industrial gearbox, or in a wind turbine. In conjunction with the aforementioned advantages, this also enables more sustainable operation of dynamically highly loaded systems and industrial gearboxes, for example, in wind turbines.

[0050] This involves the active force- and / or displacement-controlled regulation of a righting or support force exerted on the second housing and derived via the first housing, for example by means of an adjustable unit acting between the first and second housings. This control is achieved, for example, via hydraulic actuation, particularly based on instantaneous measured values ​​from at least one force / displacement sensor and / or acceleration sensor installed in the drivetrain. This also promotes sustainable operation by adapting the support method to current operating conditions.

[0051] According to one embodiment, vibration damping or decoupling is achieved by means of at least one adjustable unit at at least two opposing circumferential positions in at least one coupling section between interacting coupling parts, in particular by means of at least one preload unit per circumferential position. Depending on the application, a plurality of adjustable units can be implemented, by means of which reaction force pairs are provided about at least two or about all three moment axes or acting three-dimensionally about all three spatial directions and can optionally also be actively adjusted.

[0052] The aforementioned problem is also solved by using a drivetrain bearing arrangement described above in an industrial gearbox, particularly in a wind turbine, in an arrangement between the rotor and generator of the wind turbine, especially in a uniaxially aligned arrangement. In this arrangement, both tilting moments and torques are transmitted from the gearbox housing of the drivetrain bearing arrangement to the rotor bearing housing mounted on a shaft of the drivetrain by means of a torque support. The gearbox housing and any other flanged / coupled components, such as a generator, are supported exclusively on the rotor bearing housing. This allows the advantages mentioned above to be realized. BRIEF DESCRIPTION OF THE FIGURES

[0053] The following drawings describe the invention in more detail by way of example with reference to preferred embodiments, wherein the features shown below can represent an aspect of the invention both individually and in combination, and where reference numerals not explicitly described in a particular drawing are made to the other drawings. The drawings show, in schematic representation: Figures 1A, 1B in a side view and in a partially cut-away side view a drive train with a drive train support according to the prior art; Figure 2 in a partially cut side view a drivetrain bearing arrangement according to a first embodiment in particular for a rotor of a wind turbine; Figure 3in a partially cut side view a drivetrain bearing arrangement according to a further embodiment in particular for a rotor of a wind turbine; Figures 4A , 4B in a side view and in a cutaway front view a drivetrain bearing arrangement according to a further embodiment, in particular for a rotor of a wind turbine; Figures 5A , 5B in a side view and in a cutaway front view a drivetrain bearing arrangement according to a further embodiment, in particular for a rotor of a wind turbine; DETAILED DESCRIPTION OF THE FIGURES

[0054] The invention will first be explained with general reference to all reference numerals and figures. Specific features or individual aspects, or aspects of the present invention that are clearly visible / representable in the respective figure, will be addressed individually in connection with that figure.

[0055] A drivetrain, for example, comprises the following components: hub 1, shaft 2 (especially the rotor shaft of a wind turbine), rotor bearing housing 3, rotor bearing / rotor bearing 4 (especially torque bearing or tapered roller bearing), coupling 5, gearbox 6 in gearbox housing 7, torque support unit or weight force support 8 with coupling to the base (machine carrier), and a generator 9. Under strong, even dynamic, forces, such as bending moments generated by a rotor of a wind turbine coupled to the shaft, the drivetrain structure is subjected to high loads in conjunction with high weight forces, even if the torque support unit or weight force support 8 is comparatively well-designed / dimensioned. In addition to the rotor shaft, the flange connection to the planet carrier, the planet carrier bearings, and the torque support, the machine carrier is also subjected to considerable loads.In this context, it is of interest to create an advantageous type of drivetrain mounting that can absorb and transmit such loads effectively.

[0056] A drivetrain bearing arrangement 10 is provided, for example for industrial gearboxes 20, with a shaft 2 which is supported in a rotor bearing 14 (here: double-bearing or torque bearing). The rotor bearing 14 is enclosed or surrounded by a rotor bearing housing 13 (first housing). A gearbox component 16, in particular with a planetary gear stage, is arranged in a gearbox housing 17 (second housing), and the shaft 2 interacts with this gearbox component 16. A torque support 18 (torque and / or tilting moment support) is provided as a type of mechanical / hydraulic bridge between the two housings 13, 17, in particular at a connection (diameter) located as radially outward as possible, with support on the first housing 13 occurring, for example, at the points P1, P2 shown.The support in area P1 can advantageously also be symmetrical but off-center, in particular to ensure a support and / or damping function also in the yaw direction (perpendicular to the tilting and axial direction, rotational movement around the tower axis).

[0057] The following components are provided in particular for support on the first housing 13: tie rod 13.5, pin / cam 13.7

[0058] For support on the second housing 17 (or force transmission from the second housing) the following components are provided in particular: radially projecting flange 17.1 or the like, force application ring or segment or pin, individual force application segment 17.3 (in particular nose or tab or web), tie rod 17.5, pin / cam 17.7.

[0059] The moment support 18 enables the absorption and transmission of force from the gearbox housing 17 via the bearing housing 13 to a base 101. This provides a righting force F1 acting against the weight / gravitational force g on the gearbox housing 17 (in particular as a force couple around the central longitudinal axis or shaft axis), in the form of a tilting moment. M1 effective restoring support torque M2. Optionally, the moment support 18 can also provide a support force F2 cause, provide, or actively generate the torque acting on the transmission component and transmitted to the transmission housing. M3 This can be counteracted. The righting force F1 and the supporting force F2 They can optionally be actively controlled, for example based on current measured values ​​from force / displacement sensors at the respective interface.

[0060] The moment support 18 preferably has at least one adjustable unit 18.1, in particular comprising: preload unit 18.2 (in particular axial, in particular with at least one mechanical spring), support unit 18.3 (in particular ring-shaped or half- / shell-shaped), diagonal linkage 18.5, further support unit 18.6 (in particular ring-shaped or half- / shell-shaped), further preload unit 18.7 or at least one correspondingly installed decoupling element (in particular arranged in the radial plane and / or aligned in the circumferential direction);

[0061] Optionally, the type of support can be actively set and controlled. For this purpose, at least one force / displacement sensor 19 can optionally be provided, which can be connected to a control unit.

[0062] The drivetrain mounting arrangement 10 described here provides the advantages described here in a particularly noticeable way, especially in the case of a wind turbine 100, wherein a machine carrier or the like base 101 for the drivetrain is arranged on a tower 102.

[0063] The invention will now be explained in more detail with reference to the individual figures.

[0064] In the Fig. 1 A previously known drivetrain arrangement is shown with reference to a wind turbine. A generator 9 is attached to the gearbox housing 7. The gearbox housing is supported downwards on the machine carrier 101 via a support unit 8 (torque and weight force support). Fig. 1A The rotor bearing housing 3 is shown in a side view, and in Fig. 1BThe rotor bearing housing 3 is shown in a sectional side view. The rotor shaft 2 is comparatively massive or has a large diameter, and the rotor bearing 4 is supported relatively robustly over a fairly large length of the machine carrier 101.

[0065] The weight of the gearbox and, if applicable, a generator flanged to the gearbox housing, exerts stress on the rotor shaft, the rotor bearings, the planet carrier (especially of the first gearbox stage), its planet carrier bearings, and the flange connections between the rotor shaft and gearbox. This results in a circular bending in the rotating elements, which must be adversely affected during dimensioning.

[0066] In Fig. 2 A first embodiment of the drivetrain bearing arrangement 10 is shown. The force couple generated at the flange 17.1 or corresponding radial extensions F1creates a righting force against a pitching / tilting moment M1.The adjustable unit 18.1 can optionally implement a predefined type of support or force application, or even active control, for example, based on instantaneous measured values ​​from at least one force / displacement sensor 19 and / or an acceleration sensor 21. Force transmission and support at the rotor bearing housing 13 can occur, in particular, in the areas or points P1. This support can advantageously also be symmetrical but off-center, especially to ensure a support and / or damping function in the yaw direction as well (perpendicular to the tilt and axis direction, rotational movement about the tower axis), particularly with the intermediate interposition of at least one adjustable unit 18.1 comprising at least one preload unit 18.2 in at least one coupling section between interacting coupling parts 17.1, 18.3.In conjunction with data from at least one sensor (in particular data from accelerometer 21), active damping can be generated for vibrations e.g. around the pitch or yaw axis and / or passive damping can be achieved by elastic elements.

[0067] For example, in a wind turbine with a double-bearing rotor shaft or torque bearing and a gearbox and generator connected to it, the rotating bending resulting from the weight of the gearbox-generator combination can be significantly reduced by means of the arrangement according to the invention. According to the invention, the rotating bending stress can be significantly reduced, and at the same time, tilting in the gearbox, particularly in the first planetary stage, can also be reduced; this can ultimately lead to improved load-bearing capacity of the gear teeth. Furthermore, by supporting the gearbox torque via the rotor bearing housing and also by means of a torque support in the gearbox, improved power return can be achieved with fewer negative effects from the typically differing deformation between the machine frame and the drive train (gearbox and its connection to the rotor shaft assembly).The pitching moments, particularly those caused by wind loads (in wind turbines), do not need to be supported via the machine frame and therefore do not result in additional loads. Thanks to the bearing / support method according to the invention, oversizing of the affected machine elements (rotor shaft, rotor bearings, rotor shaft flange to the planet carrier, planet carrier, planet carrier bearings, gearbox and generator housing flanges) is also unnecessary, thus generating cost and weight advantages. Additional weight force support between the generator and the machine frame is no longer required; a support structure for weight load support below the generator becomes superfluous; pitching movements of the drive train can now be absorbed or dampened via the bearing housing without unfavorable leverage forces or load superimpositions that could affect the overall structure.

[0068] An adjustable unit or at least one adjustable element, preferably located at least in the upper and / or lower region of the interface between the gearbox and rotor bearing housing, can also support the bending moment induced by the gearbox mass and, if applicable, the generator mass at the gearbox housing (torque support), preferably relative to the rotor bearing housing. The adjustable unit thus compensates for the negative effect of the bending moment on the affected machine elements and simultaneously aligns the corresponding gearbox components, e.g., a ring gear of a first planetary stage, relative to the planet carrier, thereby also ensuring improved load-bearing behavior in the gear teeth.

[0069] According to the invention, a force-fit connection can be established between the non-rotating housing parts of the gearbox and the rotor bearing housing. The bending moment resulting from the weight force is compensated by a righting force, in particular by a righting force in the form of a force couple acting on the top and bottom of the gearbox housing.

[0070] In another function, a virtually load-free axial movement along the rotor shaft axis can be generated or permitted by diagonally connecting the adjustable unit or at least one adjustable element thereof, so that the bending moment due to weight continues to be absorbed by an equally sized force couple without impeding the axial movement. In this context, diagonal connection can also refer to a comparatively soft support in the axial direction (depending on the shaft's inclination, at least approximately in the horizontal plane) and a comparatively stiff support in the vertical direction or in the tilting direction, particularly in connection with hydraulic and / or mechanical (force or position) compensation. The tilting direction is a direction of movement of the gearbox relative to the shaft, primarily caused by the force of gravity.to be understood relative to the rotor bearing housing; the tilting does not necessarily have to occur about an axis orthogonal to the shaft, but can also be a multi-axis tilting / yawing movement depending on the dynamic state.

[0071] The relief of weight and thus of the rotating bending moment achievable by means of the arrangement according to the invention is preferably carried out in those areas of the drive train, for example of a wind turbine, which are already capable of or intended to absorb high loads and bending moments, for example resulting from wind loads. Any additional strengthening or reinforcement to ensure the desired weight-bend moment relief is therefore associated with comparatively little effort and, at most, no disadvantages that might result from differing deformation behavior between the drive train and the machine frame; however, such circumstances are significantly less detrimental with the arrangement according to the invention than with a previously known weight-force support below the generator.

[0072] In Fig. 3A second embodiment of the drivetrain bearing arrangement 10 is shown, in which the moment support 18 also includes a further support unit 18.6, which is supported in the areas or points P2 on the first housing 13, and by means of which a support force oriented essentially vertically (radial / tangentially) or circumferentially is applied. F2, which oppose a (drive) torque M3 acts on the gearbox housing (with resulting support torque) M2), in particular also provided by at least one force couple at at least approximately opposite circumferential positions, in particular with intermediate interposition of at least one adjustable unit comprising at least one preload unit in at least one coupling section between interacting coupling parts 17.3, 18.6. Also with regard to this support force F2A predefined type of support or force application, or even active control, can be implemented via a corresponding adjustable unit 18.1 or by means of individual preload or decoupling elements 18.7, for example also based on instantaneous measured values ​​of at least one force / displacement sensor 19. The force transmission takes place, for example, between the rotor bearing housing and radially projecting flange sections 17.1 or similar force application ring or segment or pin on the gearbox housing, or between the rotor bearing housing and individual force application segments 17.3 on the gearbox housing, in particular lugs or tabs or webs.

[0073] The at least one adjustable unit can provide vibration damping at different circumferential positions for both a force couple F1 oriented at least approximately axially (i.e., parallel to the drivetrain axis or axis of rotation) and a force couple F2 oriented at least approximately tangentially / radially (i.e., orthogonally to the axis of rotation), or for vibration damping realized in the corresponding direction of action. Advantageously, the corresponding preload and support units act at least at approximately the 12 o'clock and 6 o'clock circumferential positions as well as at approximately the 3 o'clock and 9 o'clock circumferential positions (especially diametrically opposite each other), or at four circumferential positions, each offset by at least 90° in the circumferential direction, whereby the respective circumferential position can also be a circumferential segment or range of, for example, 10-15°, depending on the design of the corresponding coupling section.Preferably, several adjustable units are provided, each with an individual direction of action and spring / damper characteristics, and optionally also individually adjustable, controllable, and / or regulated. This facilitates a highly individualized, situation-dependent response to instantaneous dynamic and drivetrain-specific loads in multiple or even all spatial directions.

[0074] In other words, in addition to the support units / elements for the erection force, a further advantage can be achieved through moment support by combining at least two additional support elements, acting in the vertical direction and also supporting the rotor bearing housing, using moment support. Because the rotor shaft is guided by the rotor shaft bearings in the rotor bearing housing, this additional support, functionally termed torque support, experiences the same relative movements as a gearbox torque support, and no additional loads arise from absorbing the pitching loads of the turbine rotor blades. Therefore, such functional integration into, or dual function of, the moment support results in a particularly slim and force / torque / movement-tolerant design.

[0075] This can be done by the person in the Fig. 2 and 3The machine support (base) shown may also be significantly shorter or significantly shortened compared to the axial extension previously common, especially in wind turbines (no additional support point below the second housing / gearbox housing or the generator); because the connection to the base can advantageously take place in the area of ​​the rotor bearing housing (first housing), or optionally exclusively there.

[0076] This additional advantage is illustrated here by the dotted area of ​​the machine support, merely as an example. The connection between the machine support and a tower or similar underlying support can also be designed more slenderly. In this respect, the material savings potential described here is further amplified in favor of a streamlined design.

[0077] In Fig. 3A height tolerance bearing section z1 is also indicated; depending on the desired degree of freedom, the range of motion in the vertical direction can be structurally restricted and / or limited by actively and / or passively generated counterforces through preload units or the like. A person skilled in the art can optimize this range of motion z1 individually for each application, particularly in combination with an integrated damping function.

[0078] Referring to the different axes of moment action, the embodiment can be described as follows: Fig. 3 also of at least two different adjustable units 18.1 which are implemented to generate at least two different counter-moments.

[0079] In the Fig. 4A further embodiment of the drivetrain bearing arrangement 10 is shown, in which the moment support 18 also comprises both a tilting moment support and a torque support. The force transmission takes place, for example, between tie rods 13.5 on the rotor bearing (housing) and tie rods 17.5 on the gearbox (housing), or between pins / cams 13.7 on the rotor bearing (housing) and pins / cams 17.7 on the gearbox (housing). In this embodiment, the interlocking of the two housings 13, 17 can also be described / designated as a type of claw coupling, in which each of the two housings provides one of the coupling partners, in particular by the coupling elements or claws, or the tie rods and pins described above, being integrally formed in one piece on the respective housing. This also provides high robustness and can prevent unnecessary relative movements or the loosening of parts. Fig. 4AThe interlocking pins / cams of the two gearbox housings are shown, and in Fig. 4B An exemplary distribution of the individual force transmission points in the circumferential direction is shown, with six interfaces specifically provided for each of the two different support and moment / force types, repeated every 60° circumferential angle. In particular, the tie rods can advantageously be positioned symmetrically but off-center; this also advantageously ensures a support and / or damping function in the yaw direction (perpendicular to the tilting and axial direction, i.e., in the sense of a rotational movement around the tower axis), so that the planetary carrier bearings are relieved of load during vibrations, e.g., in the yaw direction.

[0080] Referring to the different axes of moment action, the embodiment can be described as follows: Fig. 4also of at least two different adjustable units 18.1 which are implemented to generate at least two different counter-moments.

[0081] In the Fig. 5 A further embodiment of the drivetrain mounting arrangement 10 is shown, in which the functionality of the moment support includes not only tilting moment support but also a particularly effective yaw moment support in the implementation shown. This type of support makes it possible to absorb and dampen vibrations, e.g., about the tower axis (yaw axis), in a particularly effective manner. Likewise, the adjustable unit 18.1, when effectively arranged in the 12 o'clock or 6 o'clock position, can be used to absorb and dampen vibrations, e.g., about the pitch / tilt axis. Fig. 5AThe corresponding interlocking pins / cams 13.7, 17.7 of the two housings are shown (comparable to the housing coupling parts already explained in connection with the previous embodiments); in addition, the tie rods 13.5, 17.5 and the lateral tension / compression anchors 13.9, 17.9 are shown in two planes aligned at least approximately orthogonally to each other; see also the Fig. 4B In Fig. 5BAn exemplary distribution of the individual force transmission points in the circumferential direction is shown, specifically illustrating the multiple functionality of the lateral, preferably maximally eccentric, tension / compression anchors 13.9, 17.9, namely as respective force transmission points in both the circumferential and axial directions. In other words, in addition to the components of the at least one adjustable unit 18.1 already described above, the arrangement 10 can also include the following further components, in particular as part of one or more of the respective adjustable units 18.1: lateral tension / compression anchors 13.9 of the rotor bearing housing, especially in the 3 o'clock and 9 o'clock positions; lateral tension / compression anchors 17.9 of the gearbox housing, especially in the 3 o'clock and 9 o'clock positions; a further preload unit 18.9; or at least one correspondingly aligned decoupling element, in particular axially aligned.This allows for particularly effective counteracting of a yaw force F3. Side note: According to the implementation shown, force F3, like force F1, is essentially an axially oriented force, but it is given a different reference symbol here because the corresponding reaction force couple generates a counter-moment about a different axis than the reaction force couple according to the force application points of force F1. In this sense, with reference to the different axes of moment action, one can also speak of at least three different adjustable units 18.1, which in the exemplary embodiment according to the... Figures 5 are realized.

[0082] It should be noted that a yaw moment support does not necessarily have to be in the manner described in the exemplary embodiment of the Figures 5 This does not have to happen, but can already be realized when, for example, the following occur in connection with the Figures 4The described tie rods 13.5, 17.5 are arranged slightly off-center, i.e., laterally eccentrically in a horizontal plane, on both sides of the central vertical axis of the drive train or shaft 2. However, this offers or enables the Figures 5 The described embodiment provides more effective damping, particularly due to the larger effective lever arm. Therefore, a circumferential position for the tie rods 13.5, 17.5 that differs from the circumferential position shown in the figures is also possible. The lateral tension / compression tie rods 13.9, 17.9, which are positioned as far off-center as possible, are nevertheless marked with a different reference numeral here, since torque transmission in the circumferential direction is also preferred at these tie rods; compare the force arrows F2 in the figure. Fig. 5A . Reference symbol list

[0083] 1 Hub 2 Shaft, in particular rotor shaft of a wind turbine 3 Rotor bearing housing 4 Rotor bearing / rotor bearing, in particular torque bearing / tapered roller bearing 5 Coupling 6 Gearbox, in particular industrial gearbox 7 Gearbox housing 8 Torque support unit or weight force support with coupling to the base 9 Generator 10 Drivetrain bearing arrangement 13 Rotor bearing housing (first housing) 13.5 Tension anchor rotor bearing (housing) in particular in the 6 o'clock and 12 o'clock area 13.7 Pin / cam rotor bearing (housing) 13.9 Lateral tension / compression anchor rotor bearing (housing) in particular in the 3 o'clock and 9 o'clock area 14 Rotor bearing / rotor bearing 16 Gearbox component, in particular with planetary gear stage 17 Gearbox housing (second housing) 17.1 Radially projecting flange or the like, force application ring or segment or pin 17.3 Individual force application segment on gearbox housing, in particular nose or tab or web 17.5 Tension anchor gearbox (housing) in particular in the area of ​​6 o'clock and 12 o'clock 17.7 Pin / cam Gearbox (housing) 17.9 Lateral tension / compression anchor Gearbox (housing) especially in the 3 o'clock and 9 o'clock positions 18 Torque support (torque and / or tilting moment support) 18.1 Adjustable unit 18.2 Preload unit (especially axial), especially with at least one mechanical spring 18.3 Support unit, especially ring- or (half-)shell-shaped 18.5 Diagonal linkage 18.6 Further support unit, especially ring- or (half-)shell-shaped 18.7 Further preload unit (or decoupling element), especially radially oriented 18.9 Further preload unit (or decoupling element), especially axially oriented 19 Force / displacement sensor 20 Industrial gearbox 21 Acceleration sensor 100 Wind turbine 101 Machine carrier or similar base 102 Tower F1 Erection force F2 Support force F3 Yaw force orcorresponding system-side reaction force g Weight force M1 Tilting moment M2 Support torque M3 (Drive) torque P1 First support point / area on the rotor bearing housing P2 Second support point / area on the rotor bearing housing z1 Height tolerance bearing section.

Claims

1. Wind power installation (100) having an industrial transmission (20), in particular having a planetary gear stage, in particular for a rotor with double mounting or momentum mounting of the wind power installation, having: - a mounting (14) for a shaft (2) of the drive train, which mounting is supported / able to be supported in a first housing (13); - a transmission component (16) which is surrounded by a second housing (17) and coupled to the shaft (2) and configured with a planetary gear stage; - a generator (9) supported on the second housing (17), wherein the transmission-generator combination is arranged as a free end of the drive train floating in space, and - a torque support (18) which is provided as a mechanical / hydraulic bridge between the first and the second housing (13, 17) and counteracts a gravity-induced (tilting moment) torque (M1) which acts on the shaft (1) by means of the transmission component (16); wherein the torque support (18) is fastened to the first housing (13), wherein the torque support (18) has at least one adjustable unit (18.1).

2. Wind power installation (100) according to Claim 1, characterized in that the at least one adjustable unit on at least one circumferential position pairing, in particular at 6 and 12 o'clock and / or at 3 and 9 o'clock, generates a first force pair (F1) which is substantially axially aligned about the axial centre of the drive train, in particular a force pair (F1) that is directed counter to tilting and / or yawing moments; and / or in that the at least one adjustable unit on at least one circumferential position pairing, in particular at 3 and 9 o'clock and / or at 6 and 12 o'clock, generates a second torque-generating force pair (F2) which is substantially radially / tangentially aligned and acts orthogonally in relation to the axial centre of the drive train, in particular a force pair (F2) that is directed counter to torques.

3. Wind power installation (100) according to Claim 1 or 2, characterized in that the at least one adjustable unit on at least two mutually opposite circumferential positions ensures vibration damping or vibration decoupling between interacting coupling parts in at least one coupling portion, in particular by means of at least one pre-tensioning unit per circumferential position.

4. Wind power installation (100) according to one of the preceding claims characterized in that the at least one adjustable unit (18.1) on at least two mutually opposite predefined circumferential positions, in particular at least on the circumferential positions 6 and 12 o'clock and / or at 3 and 9 o'clock, acts, or is installed there so as to act, in each case in a resilient and / or damping manner between traction members or traction members / compression tappet of the transmission housing and of the rotor bearing housing.

5. Wind power installation (100) according to one of the preceding claims, characterized in that the drive train mounting assembly comprises a plurality of adjustable units by means of which reactive force pairs acting about all three momentum axes, or acting three-dimensionally about all three spatial directions, are provided and optionally are also actively adjusted.

6. Wind power installation (100) according to one of the preceding claims, characterized in that the torque support (18) is supported exclusively on the first housing (13), independently of any connection to a machine support or similar base (101) disposed below the drive train or below the drive train mounting assembly (10).

7. Wind power installation (100) according to one of the preceding claims, characterized in that the torque support (18) is supported on the first housing (13) in support points / regions disposed along an outer connection diameter between the first and the second housing, in particular in at least four circumferential portions or fully circumferentially, in particular in the case of a rotationally symmetrical distribution of the support points / regions across the entire circumference; and / or wherein the first and / or the second housing (13, 17) provide / provides at least partially at least one coupling partner for the mutual support of the housing on one another, in particular in an integral design embodiment in one piece on an external shell face of the respective housing.

8. Wind power installation (100) according to one of the preceding claims, characterized in that the at least one adjustable unit (18.1) is a unit which is adjustable in terms of force and / or direction of action and / or force-engagement point / region.

9. Wind power installation (100) according to one of the preceding claims, characterized in that the torque support (18), in particular the at least one adjustable unit (18.1) of the torque support, is provided in an upper region and / or in a lower region of an interface between the housings (13, 17); and / or wherein the torque support (18), in particular the at least one adjustable unit (18.1), is diagonally connected, in particular in such a manner that a hydraulic or mechanical compensation is relatively soft(er) in the axial direction and relatively stiff(er) in the tilting direction.

10. Wind power installation (100) according to one of the preceding claims, characterized in that a radially projecting flange or similar force-engagement collar or segment (17.1), which is delimited or encompassed, in particular in an annular manner, on at least one axial position by the torque support (18), in particular by the adjustable unit (18.1), is provided on the second housing (17).

11. Wind power installation (100) according to one of the preceding claims, characterized in that the torque support (18) is disposed in such a manner that an erection force (F1) acting substantially axially and counter to the tilting moment is provided so as to engage on the second housing (17); and / or wherein the torque support (18) is disposed in such a manner that a supporting force (F1) which acts substantially axially but symmetrically eccentrically so as to counteract a yawing moment is provided so as to engage on the second housing (17).

12. Wind power installation (100) according to one of the preceding claims, characterized in that the torque support (18) comprises a support unit (18.3) which acts on the first housing (13) and is disposed in such a manner that a force that acts substantially vertically or in the circumferential direction is provided so as to engage on the second housing (17).

13. Wind power installation (100) according to one of the preceding claims, characterized in that the transmission component (16) is disposed between the shaft (2) and a generator (9) which engages on the second housing (17) or on the transmission component (16).

14. Method for adjusting a mounting of a wind power installation having an industrial transmission according to one of Claims 1 to 13, in particular in a drive train having a rotor with double mounting or momentum mounting of a wind power installation (100), wherein a mounting (14) of a shaft (2) of the drive train which is supported in a first housing (13), and a transmission component (16) which is surrounded by a second housing (17) and coupled to the shaft (2), are mounted in relation to one another, wherein supporting the second housing (17) and thus the transmission component on the first housing (13) is performed by means of a torque support (18) that counteracts a gravity-induced torque (M1) which acts on the shaft (2) by means of the transmission component (16), in particular in a drive train having a generator (9) which is supported on the second housing (17), wherein an active force-controlled and / or path-controlled feedback-control of an erection force (F1) or supporting force (F2) exerted on the second housing (17) and dissipated by way of the first housing (13) is performed by means of at least one adjustable unit (18.1) that acts between the first and the second housing (13, 17), in a wind power installation having an industrial transmission according to one of Claims 1 to 13.

15. Method according to the preceding method claim, wherein vibration damping or vibration decoupling is performed on at least two mutually opposite circumferential positions in at least one coupling portion between interacting coupling parts by means of the at least one adjustable unit, in particular by means of at least one pre-tensioning unit per circumferential position.

16. Method according to one of the preceding method claims, wherein the active force-controlled and / or path-controlled feedback-control of a / the erection force (F1) or supporting force (F2) is performed by means of the at least one adjustable unit (18.1) based on momentary measured values of at least one force / path sensor (19) and / or acceleration sensor (21) installed in the drive train.

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